JPWO2018198322A1 - Refrigeration cycle apparatus and electrical equipment provided with the refrigeration cycle apparatus - Google Patents

Abstract

The refrigeration cycle device includes a refrigerant circuit in which a compressor, a first heat exchanger, an expansion device, and a second heat exchanger are connected by a refrigerant pipe. The refrigerant circuit including the refrigerant pipe flows so as to flow through the branch part of the refrigerant pipe, the bent part of the refrigerant pipe, the expansion device, and at least one outer surface of the refrigerant pipe connected to the expansion device. The sound suppressing member is arranged.

Description

  The present invention relates to a refrigeration cycle apparatus configured to reduce refrigerant flow noise generated from a refrigerant circuit, and an electrical apparatus including the refrigeration cycle apparatus.

  For example, as described in Patent Document 1, in an electronic expansion valve which is an example of an expansion device, the needle valve vibrates due to liquid refrigerant flowing from a direction orthogonal to the needle valve, and a large vibration sound is generated. To do. Therefore, in the technique described in Patent Document 1, the liquid refrigerant inlet is displaced to prevent the liquid refrigerant from directly colliding with the needle valve, thereby suppressing vibrations generated by the electronic expansion valve. I am doing so.

  However, depending on the operating conditions, the gas-phase refrigerant contained in the gas-liquid two-phase refrigerant may be in the form of bubbles (very small microbubbles). I can't do it. In other words, when the gas-phase refrigerant in the microbubble state passes through the throttle portion of the electronic expansion valve, it collides with the throttle portion and the structure, thereby rupturing and generating a strong destructive force. . Since the gas-phase refrigerant is a mass of compressed air unique to microbubbles, a powerful destructive force is generated by bursting. This is related to a known cavitation phenomenon.

  Therefore, Patent Document 2 discloses a technique for reducing a sudden pressure change of the refrigerant immediately after flowing out of the electronic expansion valve and reducing vibration due to cavitation (hereinafter referred to as cavitation noise). Furthermore, Patent Document 2 also suppresses vibration generated by the electronic expansion valve by winding a rubber vibration-proof material around the pipe.

  Patent Document 3 discloses a technique in which a refrigerant flow noise is reduced by forming a part or all of a conduit with a sound transmitting material and providing a sound absorbing material on the outer periphery of the sound transmitting material. Has been.

Japanese Patent No. 3533333 JP-A-9-133434 JP-A-6-194006

As in the technique of Patent Document 2, conventionally, the cavitation noise is reduced by taking measures to suppress the cavitation noise with respect to the specific operation condition in which the cavitation noise is generated.
However, even if cavitation noise is reduced, the refrigerant flow noise generated from the refrigerant circuit of the refrigeration cycle apparatus has not disappeared.

  As a result of examining the reason, the refrigerant flow sound generated from the refrigerant circuit includes not only noise and cavitation noise caused by vibration of the needle valve, which is also studied in the prior art, but also sound transmitted from the inside of the pipe to the outside of the pipe, that is, It turns out that "acoustic phenomenon" is involved. That is, as in the prior art, simply taking countermeasures against vibration has not been a countermeasure against all the refrigerant flow noises associated with the refrigerant flow.

  In addition, when part or all of the conduit is intentionally formed of a sound-transmitting material as in the technique of Patent Document 3, the sound-transmitting material cannot withstand the pressure in the conduit, and the conduit may be damaged. It will be high. For this reason, Patent Document 3 has resulted in a problem in the refrigerant circulation itself.

  As described above, the refrigerant flow sound generated in the refrigerant circuit of the refrigeration cycle apparatus is caused by the state of the refrigerant flowing in the pipe in addition to the vibration sound generated by the member vibrating by the refrigerant flowing in the pipe. Transmitted sound that passes from the inside of the pipe to the outside of the pipe. Therefore, only the vibration propagation as in the prior art can reduce only the propagation of vibration, and not all refrigerant flow noises can be reduced.

  The present invention has been made against the background of the above-mentioned problems, and has taken measures against transmitted sound transmitted from the inside of the refrigerant pipe to the outside of the refrigerant pipe due to the state of the refrigerant flowing in the refrigerant pipe. It is an object of the present invention to provide a refrigeration cycle apparatus capable of reducing flow noise and an electric device including the refrigeration cycle apparatus.

  The refrigeration cycle apparatus according to the present invention includes a refrigerant circuit in which a compressor, a first heat exchanger, an expansion device, and a second heat exchanger are connected by a refrigerant pipe, and the refrigerant circuit has a refrigerant that changes in two phases. And the refrigerant flows through the refrigerant circuit including the refrigerant pipe, and is connected to a branch portion of the refrigerant pipe, a bent portion of the refrigerant pipe, the expansion device, and the expansion device. The transmitted sound suppressing member is disposed on at least one outer surface of the refrigerant pipe.

  An electrical apparatus according to the present invention includes the above-described refrigeration cycle apparatus.

  According to the refrigeration cycle apparatus according to the present invention, the transmitted sound suppression member is arranged on the outer surface portion of the refrigerant circuit where the phase of the refrigerant changes, resulting in the state of the refrigerant flowing in the refrigerant pipe by the transmitted sound suppression member. Transmission sound transmitted from the inside of the refrigerant pipe to the outside of the refrigerant pipe can be suppressed, and as a result, the refrigerant flow noise can be reduced.

  According to the electric apparatus according to the present invention, since the refrigeration cycle apparatus is provided, the refrigerant flow noise generated in the refrigerant circuit is effectively reduced.

It is a schematic block diagram which shows an example of the refrigerant circuit structure of the refrigeration cycle apparatus which concerns on embodiment of this invention. It is a schematic diagram for demonstrating the refrigerant | coolant flow sound which generate | occur | produces in the branch part of refrigerant | coolant piping. It is a schematic diagram for demonstrating the refrigerant | coolant flow sound which generate | occur | produces in the bending part of refrigerant | coolant piping. It is a schematic diagram for demonstrating the refrigerant | coolant flow sound which generate | occur | produces with an electronic expansion valve. It is a schematic diagram for demonstrating the refrigerant | coolant flow sound which generate | occur | produces in a divider | distributor. It is a schematic diagram for demonstrating the refrigerant | coolant flow sound which generate | occur | produces in a rectifier pipe (capillary tube). It is a schematic sectional drawing which shows typically the example of a structure of the electronic expansion valve which is an example of the expansion apparatus with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is explanatory drawing for demonstrating the refrigerant | coolant flow sound which generate | occur | produces from the refrigerant circuit of the refrigerating-cycle apparatus which concerns on embodiment of this invention. It is a schematic fragmentary sectional view which shows typically the state in which the gas-liquid two-phase refrigerant | coolant is flowing into the electronic expansion valve and 1st piping with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is equipped. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a schematic sectional drawing which shows typically the structural example of the permeation | transmission sound suppression member with which the refrigerating-cycle apparatus which concerns on embodiment of this invention is provided. It is a graph which shows an example of the result of having measured the piping vibration within 50 mm from the electronic expansion valve at the time of installing the transmitted sound suppression member in the refrigerating cycle device concerning an embodiment of the invention. It is a graph for demonstrating the characteristic of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided. It is the schematic which shows typically the example of the attachment method of the permeation | transmission sound suppression member with which the refrigeration cycle apparatus which concerns on embodiment of this invention is provided.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Further, in the following drawings including FIG. 1, the same reference numerals denote the same or equivalent parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

  FIG. 1 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus 100 according to an embodiment of the present invention. In addition, in FIG. 1, the case where the refrigerating cycle apparatus 100 is provided in the air conditioning apparatus which is an example of an electric equipment is shown as an example. Moreover, in FIG. 1, the flow of the refrigerant | coolant at the time of air_conditionaing | cooling operation is shown by the solid line arrow, and the flow of the refrigerant | coolant at the time of heating operation is shown by the broken line arrow.

<Configuration of refrigeration cycle apparatus 100>
As shown in FIG. 1, the refrigeration cycle apparatus 100 includes a compressor 1, a flow path switching device 2, a first heat exchanger (heat source side heat exchanger) 3, a first distributor 4, an expansion device 5, and a second heat. An exchanger (load side heat exchanger) 6 and a second distributor 7 are provided with a refrigerant circuit connected by a refrigerant pipe 15.
In FIG. 1, the flow switching device 2 is provided and the refrigeration cycle device 100 capable of switching between the cooling operation and the heating operation by the flow switching device 2 is illustrated as an example, but the flow switching device 2 is not provided. Alternatively, the refrigerant flow may be constant.

  The compressor 1, the flow path switching device 2, the first heat exchanger 3, and the expansion device 5 are mounted on, for example, a heat source side unit (outdoor unit) 100A. The heat source side unit 100A is installed in a space (for example, outdoors) different from the air-conditioning target space, and has a function of supplying cold or warm heat to the load side unit 100B.

  The second heat exchanger 6 is mounted on, for example, a load side unit (use side unit, indoor unit) 100B. The load-side unit 100B is installed in a space (for example, indoors) that supplies cold or hot heat to the air-conditioning target space, and has a function of cooling or heating the air-conditioning target space with the cold or hot heat supplied from the heat source-side unit 100A.

  The compressor 1 compresses and discharges the refrigerant. The compressor 1 can be comprised by a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor etc., for example. When the first heat exchanger 3 functions as a condenser, the refrigerant discharged from the compressor 1 passes through the refrigerant pipe 15 and is sent to the first heat exchanger 3. When the first heat exchanger 3 functions as an evaporator, the refrigerant discharged from the compressor 1 passes through the refrigerant pipe 15 and is sent to the second heat exchanger 6.

  The flow path switching device 2 is provided on the discharge side of the compressor 1 and switches the refrigerant flow between the heating operation and the cooling operation. The flow path switching device 2 can be configured by, for example, a four-way valve, a three-way valve, or a combination of two-way valves.

The first heat exchanger 3 functions as an evaporator during heating operation and functions as a condenser during cooling operation. The 1st heat exchanger 3 can be comprised by a fin and tube type heat exchanger, for example.
A first blower 16 is attached to the first heat exchanger 3. The first blower 16 supplies air that is a heat exchange fluid to the first heat exchanger 3. The 1st air blower 16 can be comprised with the propeller fan which has a some wing | blade, for example.

  The 1st divider | distributor 4 is provided between the 1st heat exchanger 3 and the expansion apparatus 5, collects the flow of the several refrigerant | coolant which flowed out from the 1st heat exchanger 3, and is 1st heat exchanger. The flow of the refrigerant flowing into 3 is branched into a plurality. That is, at least one split flow channel is formed inside the first distributor 4, and the first distributor 4 joins the refrigerant or diverts the refrigerant.

  The expansion device 5 depressurizes the refrigerant that has passed through the second heat exchanger 6 or the first heat exchanger 3. The expansion device 5 may be mounted not on the heat source side unit 100A but on the load side unit 100B. The expansion device 5 can be configured by an electronic expansion valve, a capillary tube, or the like.

The second heat exchanger 6 functions as a condenser during the heating operation, and functions as an evaporator during the cooling operation. The second heat exchanger 6 can be constituted by, for example, a fin-and-tube heat exchanger.
A second blower 17 is attached to the second heat exchanger 6. The second blower 17 supplies air that is a heat exchange fluid to the second heat exchanger 6. The 2nd air blower 17 can be comprised with the propeller fan which has a some wing | blade, for example.

The second distributor 7 is provided between the second heat exchanger 6 and the compressor 1, collects a plurality of refrigerant flows flowing out from the second heat exchanger 6 into one, and also serves as a second heat exchanger. The flow of the refrigerant flowing into 6 is branched into a plurality. That is, at least one split flow channel is formed inside the second distributor 7, and the second distributor 7 joins the refrigerant or diverts the refrigerant.
The second distributor 7 may be the same type as the first distributor 4 or a different type.

<Operation of the refrigeration cycle apparatus 100>
Next, operation | movement of the refrigerating-cycle apparatus 100 is demonstrated with the flow of a refrigerant | coolant. Here, the operation of the refrigeration cycle apparatus 100 will be described by taking as an example a case where the heat exchange fluid is air and the heat exchange fluid is a refrigerant.

First, the cooling operation performed by the refrigeration cycle apparatus 100 will be described.
By driving the compressor 1, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 1. Hereinafter, the refrigerant flows according to solid arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 1 flows into the first heat exchanger 3 functioning as a condenser via the flow path switching device 2. In the first heat exchanger 3, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the first blower 16, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid. Refrigerant (single phase).

  The high-pressure liquid refrigerant sent out from the first heat exchanger 3 is converted into a gas-liquid two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 5. The gas-liquid two-phase refrigerant flows into the second heat exchanger 6 that functions as an evaporator. In the second heat exchanger 6, heat exchange is performed between the flowing gas-liquid two-phase refrigerant and the air supplied by the second blower 17, and the liquid refrigerant in the gas-liquid two-phase refrigerant evaporates. It becomes a low-pressure gas refrigerant (single phase). The air-conditioning target space is cooled by this heat exchange. The low-pressure gas refrigerant sent out from the second heat exchanger 6 flows into the compressor 1 via the flow path switching device 2, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Thereafter, this cycle is repeated.

Next, the heating operation performed by the refrigeration cycle apparatus 100 will be described.
By driving the compressor 1, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 1. Hereinafter, the refrigerant flows according to the broken line arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 1 flows into the second heat exchanger 6 functioning as a condenser via the flow path switching device 2 and the second distributor 7. In the second heat exchanger 6, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the second blower 17, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid. Refrigerant (single phase). The air-conditioning target space is heated by this heat exchange.

  The high-pressure liquid refrigerant sent out from the second heat exchanger 6 becomes a gas-liquid two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 5. The gas-liquid two-phase refrigerant flows into the first heat exchanger 3 functioning as an evaporator via the first distributor 4. In the first heat exchanger 3, heat exchange is performed between the flowing gas-liquid two-phase refrigerant and the air supplied by the first blower 16, and the liquid refrigerant in the gas-liquid two-phase refrigerant evaporates. It becomes a low-pressure gas refrigerant (single phase). The low-pressure gas refrigerant sent out from the first heat exchanger 3 flows into the compressor 1 via the flow path switching device 2, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 1 again. Thereafter, this cycle is repeated.

<Examples of parts that generate refrigerant flow noise>
FIG. 2 is a schematic diagram for explaining refrigerant flow noise generated at a branch portion of the refrigerant pipe. FIG. 3 is a schematic diagram for explaining the refrigerant flow noise generated at the bent portion of the refrigerant pipe. FIG. 4 is a schematic diagram for explaining refrigerant flow noise generated in the electronic expansion valve. FIG. 5 is a schematic diagram for explaining refrigerant flow noise generated in the distributor. FIG. 6 is a schematic diagram for explaining refrigerant flow noise generated in a rectifier tube (capillary tube).
The refrigerant flow noise generated from the refrigerant circuit of the refrigeration cycle apparatus 100 will be described with reference to FIGS.

  When the refrigerant flows through the refrigerant circuit, vibration sound and transmitted sound are generated mainly due to the state of the refrigerant when the phase state of the refrigerant changes. Examples of locations where the phase state of the refrigerant changes include, for example, a branch portion of the refrigerant pipe shown in FIG. 2, a bent portion of the refrigerant pipe shown in FIG. 3, an electronic expansion valve shown in FIG. 4, a distributor shown in FIG. The rectifier tube shown in FIG. The part illustrated in FIGS. 2 to 6 is a part that becomes a pressure changing part in the refrigerant circuit, and is a part where the phase state of the refrigerant changing in two layers changes.

As schematically shown in FIG. 2, when the refrigerant flowing from the left side of the paper is split into two at the branch portion, the refrigerant pipe 15 </ b> X vibrates at the branch portion, and vibration noise is generated. In addition, a transmitted sound that is transmitted to the outside of the refrigerant pipe 15X at the branch portion is generated.
In FIG. 2, the refrigerant pipe is illustrated as the refrigerant pipe 15X, the flow of the refrigerant is indicated by a white arrow, and the propagation of vibration sound and transmitted sound is indicated by a solid arrow. In FIG. 2, the vibration generation part is represented by a wavy line, and the transmitted sound generation part is represented by a spiral arrow.

As schematically shown in FIG. 3, when the refrigerant flowing from the left side of the paper is bent in the lower side of the paper, the refrigerant pipe 15 </ b> X vibrates at the bent portion, and vibration noise is generated. Further, a transmitted sound that is transmitted to the outside of the refrigerant pipe 15X at the bent portion is generated. That is, the bent portion of the refrigerant pipe 15X becomes the pressure change portion of the refrigerant circuit.
In FIG. 3, the refrigerant pipe is illustrated as the refrigerant pipe 15X, the flow of the refrigerant is indicated by a white arrow, and the propagation of vibration sound and transmitted sound is indicated by a solid line arrow. Further, in FIG. 3, the vibration generation part is represented by a wavy line, and the transmitted sound generation part is represented by a spiral arrow.

As schematically shown in FIG. 4, when the electronic expansion valve 5X is used as the expansion device 5, the electronic expansion valve 5X and the refrigerant pipe 15X vibrate and generate a vibration sound when the refrigerant passes through the throttle portion 54X. To do. In addition, a transmission sound that is transmitted to the outside of the refrigerant pipe 15X by the refrigerant pipe 15X connected to the electronic expansion valve 5X is generated. That is, the electronic expansion valve 5X and the refrigerant pipe 15X connected to the electronic expansion valve 5X serve as a pressure change part of the refrigerant circuit.
In FIG. 4, the electronic expansion valve is shown as an electronic expansion valve 5X, the refrigerant pipe is shown as a refrigerant pipe 15X, the flow of the refrigerant is shown by white arrows, and the propagation of vibration sound and transmitted sound is shown by solid arrows. ing. Further, in FIG. 4, the portion where vibration is generated is represented by a wavy line, and the portion where transmitted sound is generated is represented by a spiral arrow.

As schematically shown in FIG. 5, when a distributor 4X that divides the refrigerant flow into a plurality of parts is used, the refrigerant that has flowed from the lower side of the page flows into the mixed flow passage 4X-1 of the distributor 4X. In addition, the distributor 4X and the refrigerant pipe 15X vibrate, and vibration noise is generated. Moreover, the permeation | transmission sound which permeate | transmits the exterior of the refrigerant | coolant piping 15X in the split mixing flow path 4X-1 generate | occur | produces.
In FIG. 5, the distributor is shown as a distributor 4X, the refrigerant pipe is shown as a refrigerant pipe 15X, the flow of the refrigerant is shown by white arrows, and the propagation of vibration sound and transmitted sound is shown by solid arrows. . Further, in FIG. 5, the vibration generation part is represented by a wavy line, and the transmitted sound generation part is represented by a spiral arrow.

As schematically shown in FIG. 6, when the rectifying pipe 5Y is used as the expansion device 5, the rectifying pipe 5Y vibrates in the portion where the refrigerant flowing from the lower side of the paper flows into the rectifying tube 5Y and the portion where the refrigerant flows out. And vibration noise is generated. In addition, a transmission sound that is transmitted to the outside of the refrigerant pipe 15X is generated at a portion where the refrigerant flows out.
In FIG. 6, the rectifying pipe is illustrated as the rectifying pipe 5 </ b> Y, the refrigerant pipe is illustrated as the refrigerant pipe 15 </ b> X, the flow of the refrigerant is illustrated with white arrows, and the vibration sound and the transmitted sound are illustrated with solid line arrows. Further, in FIG. 6, the portion where vibration is generated is represented by a wavy line, and the portion where transmitted sound is generated is represented by a spiral arrow.

<Specific configuration of electronic expansion valve 5X>
FIG. 7 is a schematic cross-sectional view schematically showing a configuration example of an electronic expansion valve 5X which is an example of the expansion device 5 provided in the refrigeration cycle apparatus 100. Based on FIG. 7, the structure of the electronic expansion valve 5X is demonstrated. In FIG. 7, among the refrigerant pipes 15X connected to the electronic expansion valve 5X, the refrigerant pipe 15X connected on the extension in the moving direction when adjusting the refrigerant flow rate of the valve body 52X of the electronic expansion valve 5X is shown. A refrigerant pipe 15X that is illustrated as a first pipe 15AX and connected so as to be orthogonal to the moving direction of the valve body 52X of the electronic expansion valve 5X is illustrated as a second pipe 15BX.

The electronic expansion valve 5X includes a main body 51X, a valve body 52X that is movably provided inside the main body 51X, and a driving device 59X that drives the valve body 52X.
The main body 51X is formed by cutting a brass casting, for example. Inside the main body 51X, a valve chamber 55X is formed in which a valve body 52X is provided so as to freely advance and retract. The refrigerant flows into the valve chamber 55X. The second pipe 15BX is connected to a side surface of the main body 51X (a wall portion at a position orthogonal to the moving direction of the valve body 52X). The second pipe 15BX communicates with the valve chamber 55X through a through hole 57X formed in the side surface of the main body 51X. That is, the through hole 57X functions as a refrigerant outlet / inlet.

  The first pipe 15AX is connected to the bottom part of the main body 51X (the wall part on the extension of the moving direction of the valve body 52X). The first pipe 15AX communicates with the valve chamber 55X through a through hole 56X formed at the bottom of the main body 51X. That is, the through hole 56X functions as a refrigerant outlet / inlet. The peripheral portion of the through hole 56X on the valve chamber 55X side functions as the valve seat 53X.

  In the valve body 52X, a cylindrical portion 52aX and a conical portion 52bX are integrally formed, and are provided so as to be able to advance and retract toward the through hole 56X. The columnar portion 52aX constitutes the shaft portion of the valve body 52X and is connected to the drive device 59X. When the tip of the conical portion 52bX is inserted into and extracted from the through hole 56X, the conical portion 52bX and the valve seat 53X form an annular throttle portion 54X. That is, by moving the valve body 52X forward and backward, the opening area of the throttle portion 54X is changed, and the refrigerant flow rate can be adjusted. Note that the conical portion 52bX does not have to be strictly conical, and may be a tapered shape (a shape that decreases in diameter toward the first pipe 15AX).

  The drive device 59X is provided on the opposite side of the main body 51X from the first pipe 15AX. By the drive device 59X, the valve body 52X moves in the left-right direction on the paper surface in the valve chamber 55X. The passage area (cross-sectional area of the passage) of the throttle portion 54X, which is an annular minute passage formed by the valve seat 53X and the valve body 52X, changes depending on the position of the valve body 52X. That is, the opening degree of the through hole 56X is adjusted by the position of the valve body 52X.

  The operation of the electronic expansion valve 5X configured as described above will be described. When the electronic expansion valve 5X is applied as the expansion device 5 of the refrigeration cycle apparatus 100, the electronic expansion valve 5X is disposed between the first heat exchanger 3 and the second heat exchanger 6 as one component of the refrigeration cycle apparatus 100. Installed. Therefore, the gas-liquid two-phase refrigerant flows in from the first pipe 15AX or the second pipe 15BX by installing the electronic expansion valve 5X.

First, the operation of the electronic expansion valve 5X when the gas-liquid two-phase refrigerant flows from the first pipe 15AX will be described. That is, in FIG. 7, the operation of the electronic expansion valve 5X will be described by taking as an example the case where the refrigerant flows from the right side of the drawing to the left side of the drawing.
The gas-liquid two-phase refrigerant flows from the first pipe 15AX into the main body 51X of the electronic expansion valve 5X. The gas-liquid two-phase refrigerant that has flowed into the main body 51X from the first pipe 15AX collides with the valve body 52X. The valve body 52X with which the gas-liquid two-phase refrigerant has collided vibrates and generates a vibration sound.

  When the gas-liquid two-phase refrigerant flows from the second pipe 15BX, the gas-liquid two-phase refrigerant flows from the second pipe 15BX to the main body 51X of the electronic expansion valve 5X. The gas-liquid two-phase refrigerant that has flowed into the main body 51X from the second pipe 15BX collides with the valve body 52X. The valve body 52X with which the gas-liquid two-phase refrigerant has collided vibrates and generates a vibration sound. By disposing the connection position of the second pipe 15BX, the gas-liquid two-phase refrigerant can be prevented from directly colliding with the valve body 52X. However, it is not a countermeasure against cavitation noise.

The refrigerant flowing from the second pipe 15BX becomes a swirling flow around the valve body 52X in the valve chamber 55X. Therefore, the liquid refrigerant tends to be unevenly distributed on the outer peripheral side and the gas refrigerant is distributed on the inner peripheral side. Thereafter, the refrigerant flows into the throttle portion 54X after a short distance.
Generally, when the gas-liquid two-phase refrigerant flows into the electronic expansion valve 5X from the second pipe 15BX, there is a distance from the flow into the valve chamber 55X to reach the throttle portion 54X, and the refrigerant flow is disturbed.

Next, the operation of the electronic expansion valve 5X when the liquid refrigerant flows from the first pipe 15AX will be described.
The liquid refrigerant flows from the first pipe 15AX into the main body 51X of the electronic expansion valve 5X. Since only the liquid refrigerant is present in the valve chamber 55X, it is difficult for refrigerant flow noise to occur in the throttle portion 54X. However, after passing through the throttle portion 54X, gas refrigerant (bubbles) may be generated in a non-equilibrium state due to cavitation or the like. That is, cavitation noise is generated by using a gas-liquid two-phase refrigerant instead of a liquid refrigerant. Thereafter, the flow direction is changed in the valve chamber 55X, and the refrigerant is discharged from the second pipe 15BX.
The same applies when the liquid refrigerant flows from the second pipe 15BX.

  As described above, in the electronic expansion valve 5X, even if the refrigerant flows from the first pipe 15AX or the refrigerant flows from the second pipe 15BX, vibration and noise are generated in any case. .

<Details of refrigerant flow noise generated from the refrigerant circuit>
FIG. 8 is an explanatory diagram for explaining the refrigerant flow sound generated from the refrigerant circuit of the refrigeration cycle apparatus 100. FIG. 9 is a schematic partial cross-sectional view schematically showing a state in which the gas-liquid two-phase refrigerant is flowing in the electronic expansion valve 5X and the first pipe 15A included in the refrigeration cycle apparatus 100. The refrigerant flow noise generated from the refrigeration cycle apparatus 100 will be specifically described based on FIGS.

In addition, in FIG. 8, an example of the frequency characteristic of the refrigerant | coolant flow sound generated from the refrigerant circuit of the refrigerating cycle apparatus 100 is shown as a graph. In FIG. 8, the vertical axis indicates the sound pressure level (dB), and the horizontal axis indicates the frequency (Hz).
In FIG. 9, an electronic expansion valve 5X which is one of the expansion devices 5 is illustrated. The configuration of the electronic expansion valve 5X is as described in FIG.

The refrigerant flow sound generated from the refrigerant circuit of the refrigeration cycle apparatus 100 includes shocking vibration noise generated when the refrigerant passes through the electronic expansion valve 5X, and air column resonance with the refrigerant pipe 15 when the refrigerant flows through the refrigerant pipe 15. When bubbles or the like are generated in the resonance sound or the refrigerant, there are shocking vibration sounds (sounds accompanying a so-called cavitation phenomenon) according to the diameter and amount of the bubbles.
Among these sounds, there are vibration sounds that are radiated by vibrating the refrigerant pipe 15 or the components themselves, and there are transmitted sounds that are transmitted from the inside of the refrigerant pipe 15 to the outside.

  With respect to transmitted sound, it is generally known that an acoustic attenuation effect can be obtained when passing through a material surface if the thickness is ¼ wavelength. However, when the acoustic energy of the transmitted sound increases due to some influence, the transmitted sound may not be attenuated even with a thickness of ¼ wavelength. For example, there may be a case where the acoustic energy of the transmitted sound increases due to the addition of the influence of a sound density wave. When reaching the refrigerant pipe 15 having a small diameter and a long distance, there is inevitably a sparse density wave in the refrigerant pipe 15. When the dense wave and the dense part of the transmitted sound match, the acoustic energy increases due to the amplification of the sound. Thereby, in the thin refrigerant pipe 15, there is a high possibility that sound is transmitted to the outside of the refrigerant pipe 15.

  Depending on the operating conditions of the refrigeration cycle apparatus 100, the refrigerant in the refrigerant circuit flows in the order of gas phase → gas-liquid two phase → liquid phase. In addition, the refrigerant in the refrigerant circuit may flow in the order of liquid phase → gas-liquid two phase → gas phase. Under these phase conditions, different refrigerant flow sounds are generated. That is, the refrigerant flow sound generated from the gas-liquid two-phase refrigerant, the refrigerant flow sound generated from the liquid-phase refrigerant, and the refrigerant flow sound generated from the gas-phase refrigerant are different. This is due to the condition of the refrigerant that generates sound. Refrigerant flow noise is generated when the refrigerant having different phase conditions passes through or collides with the throttle portion 54X.

  The variable sound conditions are particularly created when the refrigerant is in a gas-liquid two-phase state. The gas-liquid two-phase gas phase can also be expressed as a “bubble” state aggregate composed of various size diameters. And the bubble with a very small bubble diameter is a micro class, and is called a so-called micro bubble. Further, the inside of the refrigerant pipe 15 forming the refrigerant circuit is in a high pressure state for circulating the refrigerant, and acceleration is generated in the refrigerant. When microclass bubbles are generated in a gas-liquid two-phase refrigerant flowing at high speed, the bubbles are traveling through the refrigerant pipe 15 in an accelerated state where pressure is applied. At this time, air is crushed inside the foam.

  When such a high-pressure bubble flows into the electronic expansion valve 5X and collides with the throttle portion 54X of the electronic expansion valve 5X, it bursts at the throttle portion 54X. At this time, a “sound = noise” called a bubble pulse accompanying the cavitation phenomenon occurs. As shown in FIG. 8, it was possible to analyze the frequency of the sound based on the acoustic characteristics that the frequency was 15 kHz or higher and the high frequency band = ultrasonic band.

  Depending on the diameter of the foam, the collision of the foam, and the passing state of the foam restricting portion 54X, the sound in the ultrasonic band repeatedly fluctuates, and various frequencies are generated. This frequency is generated as pipe vibration, and the vibration propagates outside the refrigerant pipe 15 as transmitted sound. The transmitted sound that has propagated to the outside of the refrigerant pipe 15 reaches the consumer as an unpleasant sound as a band that can be heard audibly. That is, a plurality of adjacent frequencies of ultrasonic waves having peak states are generated. The component of the peak ultrasonic band is a sound wave in a non-linear region, and is generated as a frequency component corresponding to a difference and a sum due to a known parametric phenomenon between adjacent frequencies.

  In particular, the difference frequency component generates a new frequency in the audible frequency band. That is, the difference frequency component propagates to the liquid-phase refrigerant or the gas-phase refrigerant flowing through the refrigerant pipe 15, and sound is generated from a part of the refrigerant circuit different from the vibration generation part. This is radiated as sound (noise) and provided as an unpleasant sound to consumers. And this phenomenon is one of the reasons why it was not possible to take measures against all the refrigerant flow noises simply by taking measures against vibration.

Further, as shown in FIG. 8, a plurality of frequencies due to cavitation are generated in an ultrasonic band of 15 kHz or more. This difference component is generated in the audible band from 1 kHz to 8 kHz. The wavelength of 15 kHz is 0.023 m (one wavelength) from the relationship of C (sound speed) = f (frequency) * λ (wavelength) when the temperature in the refrigerant pipe 15 is 20 degrees.
In the band of 15 kHz or more, the wavelength is shorter than the above value (C = 335 + 0.6 t (m / S ² )).
The wavelength of 4 kHz is the wavelength λ = 0.087 m.

  Due to the above phenomenon, the refrigerant flow noise is generated as an unpleasant sound even in the liquid phase state and the gas phase state. The frequency component that is likely to occur in the liquid phase is a band around 1 kHz. The frequency component in this case is a frequency component associated with the vortex flow and the separated flow when the liquid-phase refrigerant passes through the throttle portion 54X. Moreover, the frequency component which is easy to generate | occur | produce in a gaseous-phase state is a frequency band of 5 kHz-8 kHz. The frequency component in this case is a fluid sound component when the gas-phase refrigerant passes through the throttle portion 54X, and is basically the frequency component of the passing sound when passing through a very narrow space. In any phase, an ultrasonic band hardly occurs and an audible band component is mainly used.

  The generated sound includes sliding sound between the refrigerant pipe 15 and the refrigerant. This sliding sound includes a vibration component. For this reason, vibration countermeasures as in the conventional example are taken as countermeasures against vibration. However, the vibration countermeasures alone are not sufficient for the frequency components of the sound transmitted from the inside of the refrigerant pipe 15 to the outside and transmitted to the space. Is possible. In other words, as a measure against sound radiation that has once transmitted to the outside of the refrigerant pipe 15, an external process for performing some energy conversion process is required.

  The refrigerant flow sound in the two-phase state coincides with the pipe resonance, and causes an amplification phenomenon in the dense part of the sound density wave in the refrigerant pipe 15. Since the refrigerant pipe 15 is generally bent and mounted on the refrigeration cycle apparatus 100, it can be assumed that both ends of the refrigerant pipe 15 up to the bent portion are “closed spaces”. The density wave in this case is defined by f = nC / 2L. C is the speed of sound, n is the order, and L = spatial dimension (m).

  Assuming a two-phase state, when L = nC / 2f and 4 kHz, L = 0.044 m (about 4 cm). The refrigerant pipe 15 (first pipe 15AX) directly connected to the electronic expansion valve 5X generally has a straight pipe portion of about 5 cm, and this straight pipe portion has a sound dense portion. Will be amplified. As a result, sound amplification is performed within 5 cm of the refrigerant pipe 15 (first pipe 15AX) directly connected to the electronic expansion valve 5X. Even if only the electronic expansion valve 5X is taken, a dramatic countermeasure is taken. There is no effect.

  Therefore, in order to take a reliable measure against the refrigerant flow noise, it is necessary to apply not only to the electronic expansion valve 5X but also to the refrigerant pipe 15 (first pipe 15AX) directly connected to the electronic expansion valve 5X. Become.

<Countermeasures for refrigerant flow noise generated from refrigerant circuit>
10 to 17 are schematic cross-sectional views schematically showing a configuration example of the transmitted sound suppression member 60 included in the refrigeration cycle apparatus 100. FIG. 18 is a graph showing an example of a result of measuring pipe vibration within 50 mm from the electronic expansion valve 5X when the transmitted sound suppression member 60 is installed in the refrigeration cycle apparatus 100. Based on FIGS. 10 to 18, countermeasures for refrigerant flow noise in the refrigeration cycle apparatus 100 will be described. The transmitted sound source 80 shown in FIGS. 10 to 18 is one of the parts illustrated in FIGS.

10 and 11 show an example of the transmitted sound suppressing member 60, FIGS. 12 and 13 show another example of the transmitted sound suppressing member 60, and FIGS. 14 and 15 show still another example of the transmitted sound suppressing member 60. FIG. 16 and FIG. 17 show still another example of the transmitted sound suppressing member 60.
In FIG. 18, the vertical axis represents the vibration acceleration characteristic (G), and the horizontal axis represents the frequency (Hz).

  As described above, the sound radiation once transmitted to the outside of the refrigerant pipe 15 needs to be processed from the outside for performing some energy conversion processing. As a means for efficiently performing heat conversion, it is effective to cover the sound radiation source with a material including an air chamber. Moreover, in order to efficiently take measures against sound radiation, vibration sound and transmitted sound can be obtained with a sound absorbing layer (sound absorbing material) or a sound absorbing and damping layer (absorbing and damping material) that combines a sound absorbing layer and a damping layer. It is effective to cover the periphery of the occurrence location (see FIGS. 2 to 6). By doing so, it is possible to simultaneously perform both a countermeasure for the audible band in the sound absorbing layer and a countermeasure for the ultrasonic band in the damping layer.

  In addition, as shown in FIG. 18, there is a vibration component due to acoustic excitation due to the dense wave in the refrigerant pipe 15 in the frequency band near 6 kHz, but it protrudes to a higher frequency band than that. Such a vibration frequency component has a very small response. From this, the frequency of 14 kHz or more coincides with the air column resonance in the refrigerant pipe 15 rather than the vibration accompanying the cavitation of the bubble ruptured by the expansion device 5 is generated as a vibration sound by shaking the refrigerant pipe 15. It can be seen that there is a high possibility that it has occurred.

Therefore, in the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is provided.
The transmitted sound suppressing member 60 can be composed of a single layer of a sound absorbing material 61 as shown in FIGS. 10 and 11, for example. The sound absorbing material 61 includes an air chamber, and plays a role of consuming the sound component in the audible band by converting the frequency component in the audible band into heat energy. The sound absorbing material 61 is formed using, for example, pulp fibers as a base material. Specifically, it can be formed by compression molding bioplastics or the like that are pulp fibers. For this reason, there is no concern of causing a mesothelioma problem due to fibers scattered from the material, compared to a conventional sound absorbing material such as glass fiber.

  The pulp fiber has a plurality of air holes formed in the cross section of the fiber, includes more air chambers than those molded with other fibers, and can obtain a high sound absorption coefficient. Further, the surface of the sound absorbing material 61 may be accompanied by water repellency. If it carries out like this, it will be hard to absorb the water | moisture content which generate | occur | produces in the refrigerant | coolant piping 15, and the fall of a sound absorption performance can be suppressed. Furthermore, an anti-mold material may be included in the sound absorbing material 61. In this way, even if moisture is absorbed, generation of mold and the like can be suppressed.

That is, when the refrigeration cycle apparatus 100 is provided in an air conditioner, the ambient temperature or the temperature of the target component may be a high temperature of 50 ° C. or higher, or a low temperature near 0 ° C. Therefore, the sound absorbing material 61 is preferably provided with water resistance, water repellency, antibacterial function, and mold prevention function. Since it is also possible that the installation location will be lower than the dew point temperature, if the sound absorbing material 61 has water resistance, water repellency, antibacterial, and antifungal functions, it may fall off from the installation location, or the damping material 62 or the sound insulation material. It can suppress that it peels from 63, absorbs a water | moisture content, or mold | fungi generate | occur | produce.
Further, in order to maintain the shape of the sound absorbing material 61 even in a high temperature environment, the sound absorbing material 61 is preferably provided with heat resistance. If the sound absorbing material 61 has heat resistance, it can be prevented that the sound absorbing material 61 is peeled off from the installation location or peeled off from the vibration damping material 62 or the sound insulating material 63.

  Further, the transmitted sound suppressing member 60 can be constituted by two layers of a sound absorbing material 61 and a vibration damping material 62 as shown in FIGS. 12 and 13, for example. The sound absorbing material 61 is as described with reference to FIGS. The damping material 62 includes a dielectric material that converts vibrations into heat, and consumes acoustic components that are transmitted from the inside of the refrigerant pipe 15 to the outside as thermal energy. The damping material 62 plays the role of consuming energy by vibration-heat conversion of acoustic energy. The damping material 62 effectively attenuates the frequency components of the audible band, particularly in the ultrasonic band. The damping material 62 is formed by kneading, for example, a dielectric material such as carbon with a polyester resin or the like. Further, the vibration damping material 62 may be kneaded with a piezoelectric material or the like. If it carries out like this, it will also become possible to perform heat conversion by frictional heat.

  When the transmitted sound suppression member 60 is configured by two layers of the sound absorbing material 61 and the vibration damping material 62, the sound absorbing material 61 is provided on the inner side (the refrigerant pipe 15 side), and the vibration damping material 62 is provided on the outer side of the sound absorbing material 61. Like that. In this way, the acoustic energy component transmitted to the outside of the refrigerant pipe 15 can be reliably attenuated. And it becomes a countermeasure against all the refrigerant | coolant flow noise which generate | occur | produces, and a consumer's discomfort by an unpleasant sound can be reduced.

  Furthermore, the transmitted sound suppression member 60 can be constituted by two layers of a sound absorbing material 61 and a sound insulating material 63, as shown in FIGS. The sound absorbing material 61 is as described with reference to FIGS. The sound insulating material 63 suppresses vibration at the arrangement location. The sound insulating material 63 is made of a material that converts vibration energy into heat energy, for example, a vibration isolating member such as butyl rubber, like the vibration damping material 62, and effectively attenuates frequency components in the same or different frequency band as the vibration damping material 62. It is something to be made.

  When the transmitted sound suppression member 60 is configured by two layers of the sound absorbing material 61 and the sound insulating material 63, the sound insulating material 63 is provided on the inner side (the refrigerant pipe 15 side), and the sound absorbing material 61 is provided on the outer side of the sound insulating material 63. To do. In this way, the acoustic energy component transmitted to the outside of the refrigerant pipe 15 can be reliably attenuated. And it becomes a countermeasure against all the refrigerant | coolant flow noise which generate | occur | produces, and a consumer's discomfort by an unpleasant sound can be reduced.

  In addition, the transmitted sound suppression member 60 can be configured by three layers of a sound absorbing material 61, a vibration damping material 62, and a sound insulating material 63, for example, as shown in FIGS. 16 and 17. The sound absorbing material 61 is as described with reference to FIGS. The damping material 62 is as described with reference to FIGS. The sound insulating material 63 is as described with reference to FIGS. 14 and 15.

  When the transmitted sound suppression member 60 is configured by three layers of the sound absorbing material 61, the vibration damping material 62, and the sound insulating material 63, the sound insulating material 63 is provided on the inner side (the refrigerant pipe 15 side), and the vibration damping material 62 is provided on the outer side. The sound absorbing material 61 is provided between the vibration damping material 62 and the sound insulating material 63. In this way, the acoustic energy component transmitted to the outside of the refrigerant pipe 15 can be reliably attenuated. And it becomes a countermeasure against all the refrigerant | coolant flow noise which generate | occur | produces, and a consumer's discomfort by an unpleasant sound can be reduced.

  The transmitted sound suppression member 60 is preferably arranged so as to cover the entire circumference of the arrangement location. Further, it is not necessary to attach the transmitted sound suppressing member 60 to the outer peripheral surface of the attachment location, and there may be a gap between the surface of the transmitted sound suppressing member 60 on the piping side and the outer peripheral surface of the refrigerant piping 15. In addition, how to attach the transmitted sound suppressing member 60 will be described in detail later.

This will be described more specifically.
FIG. 19 is a graph for explaining the characteristics of the transmitted sound suppression member 60 included in the refrigeration cycle apparatus 100. In FIG. 19, the left vertical axis represents the sound absorption rate (%), the right vertical axis represents the sound insulation volume (dB), and the horizontal axis represents the frequency (Hz).

The relationship between the sound absorbing material 61 and the vibration damping material 62 is as follows.
Both the sound absorbing material 61 and the damping material 62 are related to the wavelength of the frequency band to be reduced and the output level (pressure = sound pressure level).
The sound absorbing material 61 corresponds to an audible band of 10 kHz or less.
The damping material 62 corresponds to an ultrasonic band of 10 kHz or higher.

The sound absorbing material 61 is configured as follows.
One wavelength λ = C / f (C is the speed of sound (340 m / S in the air (when the atmospheric temperature is 15 degrees)), and f is the frequency (Hz)).
For example, assuming that the frequency is reduced with a center frequency of 5 kHz, the wavelength at that time is approximately 0.068 m (about 7 cm). It is publicly known that the sound absorbing material 61 desirably has a thickness of ¼ wavelength or more of the wavelength of the frequency to be absorbed. That is, from the above calculation, when it is desired to reduce the frequency around 5 kHz, the thickness of the sound absorbing material 61 needs to be at least 1.75 cm.

  However, it is often difficult to ensure an ideal thickness with an ideal thickness and an actual home appliance (particularly a home appliance having only a small space). Therefore, it is important to secure an air chamber inside the sound absorbing material 61 in order for the sound absorbing material 61 to enhance the sound absorbing effect (increase the sound-to-heat conversion efficiency).

  The sound absorbing material 61 used as the transmitted sound suppressing member 60 may be formed by a fiber wire diameter and a manufacturing method that can secure a sound absorbing material weight ratio of the air chamber to the thickness of around 50%. For example, the sound-absorbing material 61 can be formed by a manufacturing method based on a fiber wire diameter of 100 μm or less and the lamination of the fiber material by natural dropping. Further, as the material of the sound absorbing material 61, it is preferable to use pulp fiber or the like obtained by extracting a natural pulp material in which an air layer is secured in the fiber material itself into a fiber shape.

  As a result, the thickness for installing the transmitted sound suppression member 60 can be set to, for example, 5 mm in the interior space of home appliances where only a minimal space can be provided, and a sound absorption effect of 90% or more can be achieved in the band around 5 kHz. (Line A shown in FIG. 19).

Next, the damping material 62 is configured as follows.
When the frequency approaches the ultrasonic band and the sound pressure level of the ultrasonic band has a sound pressure level equal to or greater than or equal to the audible frequency band, having a characteristic having a plurality of narrow directivity angles (directivity) It is known. Therefore, it is a well-known fact that the sound in the ultrasonic band is a sharp (strong) sound with linearity.

  Therefore, for a sound source in which sound in the ultrasonic band is generated simultaneously, the sound pressure level may not be sufficiently reduced by the sound absorbing material 61 alone. Moreover, it is difficult to reduce the sound pressure (sound pressure level) in all the wide frequency bands in the home appliances in a very small space with only the sound absorbing material 61 having a small thickness. Therefore, the transmitted sound suppressing member 60 uses a vibration damping material 62 in addition to the sound absorbing material 61 and has a two-layer structure of the sound absorbing material 61 and the vibration damping material 62.

  By using the damping material 62, it is possible to further reduce the sound pressure level of the acoustic energy in the high-frequency band with sharp directivity that has passed through and entered the sound absorbing material 61 by the heat conversion effect of the material. At this time, particularly when an ultrasonic band of 12 kHz or higher is targeted, the wavelength is 0.028 m (around 3 cm) as described above, and the quarter wavelength is 0.007 m.

  However, as described above, since an effective thickness cannot be ensured, it is necessary to obtain an effective sound insulation effect with the material contents to be configured. For this purpose, the pressure of the sound incident on the vibration damping material 62 is regarded as vibration, and the vibration damping material 62 is made of a material that effectively changes the vibration energy into thermal energy so as to ensure sound insulation performance. (Line B shown in FIG. 19). In addition, if the piezoelectric effect is used, the heat conversion efficiency can be increased, and even if the material thickness is thin, the sound is equal to or higher than that of a high-density material such as thick rubber (line C shown in FIG. 19). A reduction effect can be obtained.

  As described above, the transmitted sound suppressing member 60 can achieve sound absorption and sound insulation under a thickness condition thinner than the conventional thickness by a manufacturing method and material selection, and a kneading material for the installation space and layer structure. Depending on the characteristics, the thickness of the sound absorbing material 61 and the damping material 62 can be freely configured.

  Moreover, the sound-absorbing layer and the sound-insulating layer can be made thin by making the transmitted sound suppressing member 60 have a three-layer structure of the sound-insulating material 63, the sound-absorbing material 61, and the vibration-damping material 62. Even if the sound insulating material 63 is composed of a vibration isolating member, the frequency of sound due to vibration can be shifted and separated from the frequency band that can be attenuated by the sound absorbing material 61 and the vibration damping material 62, and the transmitted sound suppressing member 60 can be separated. Can be made thinner. For example, when a peak sound is generated with a sound in a frequency band near 2k-3 kHz caused by piping vibration, if the sound insulating material 63 can suppress or shift the generated frequency, the sound absorbing material 61 and the damping material 62 are thin. This is an effective means for restricting conditions such as limited mounting space.

<Example of how to install transmitted sound suppressing member 60>
20 to 26 are schematic views schematically showing an example of how to install the transmitted sound suppression member 60 included in the refrigeration cycle apparatus 100. FIG. A specific example of how to attach the transmitted sound suppressing member 60 will be described with reference to FIGS. 25 and 26 show a state in which the method of attaching the transmitted sound suppression member 60 of FIGS. 22 to 24 is viewed from the flow direction of the refrigerant. 25 and 26 show the transmitted sound suppression member 60 shown in FIGS. 12 and 13 as a representative example. Furthermore, the transmitted sound source 80 shown in FIGS. 20 to 24 is one of the parts illustrated in FIGS. 2 to 6.

  As shown in FIG. 20, the transmitted sound suppression member 60 is attached to the outer surface of the member to be the transmitted sound source 80 using, for example, an adhesive, so that the transmitted sound suppression member 60 is attached to the outer surface of the member to be the transmitted sound source 80. Can be attached to cover. Therefore, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure. However, it is not necessary that the entire surface of the transmitted sound suppressing member 60 is attached to the outer surface of the member that becomes the transmitted sound source 80, and even if there is a gap between the transmitted sound suppressing member 60 and the member that becomes the transmitted sound source 80. Good. There may be a case where the sound absorption effect can be further improved by the gap.

  As shown in FIG. 21, the transmitted sound suppressing member 60 covers the outer surface of the member that becomes the transmitted sound source 80, and both ends of the transmitted sound suppressing member 60 using, for example, a fixing member 70 (for example, a string, a binding band, a wire). By fixing the entire circumference of the part, the transmitted sound suppressing member 60 can be attached so as to cover the outer surface of the member that becomes the transmitted sound source 80. Therefore, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure.

  The fixed position of the transmitted sound suppressing member 60 by the fixing member 70 is avoided from the projection region R1 of the transmitted sound source 80 of the transmitted sound suppressing member 60 when the transmitted sound suppressing member 60 covers the outer surface of the member that becomes the transmitted sound source 80. To position. This is because if the fixing member 70 is installed in the projection region R1, the air chamber of the sound absorbing material 61 constituting the transmitted sound suppressing member 60 may be crushed.

  However, the number and size of the fixing members 70 are not particularly limited. Further, if the fixing member 70 is installed so as to avoid the projection region R <b> 1 of the transmitted sound suppressing member 60, the fixing member 70 may not necessarily fix both ends of the transmitted sound suppressing member 60. Further, as described above, there may be a gap between the transmitted sound suppressing member 60 and the member that becomes the transmitted sound source 80.

  As shown in FIG. 22, the transmitted sound suppression member 60 is covered with the transmitted sound suppression member 60 so as to cover a part of the transmitted sound suppression member 60 using, for example, a band 71. Can be attached so as to cover the outer surface of the member to be the transmission sound source 80. Therefore, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure. The band 71 is an example of the fixing member 70.

  As shown in FIG. 23, the transmitted sound suppression member 60 is covered with the transmitted sound suppression member 60 and the part of the transmitted sound suppression member 60 is fixed using, for example, a clip 72. Can be attached so as to cover the outer surface of the member to be the transmission sound source 80. Therefore, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure. The clip 72 is an example of the fixing member 70.

  As shown in FIG. 24, the transmitted sound suppression member 60 is covered with the transmitted sound suppression member 60 and the part of the transmitted sound suppression member 60 is fixed using, for example, a stapler 73. Can be attached so as to cover the outer surface of the member to be the transmission sound source 80. Therefore, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure. The stapler 73 is an example of the fixing member 70.

  The transmission sound suppressing member 60 shown in FIGS. 22 to 24 is assumed to be attached as shown in FIGS. 25 and 26, for example. FIG. 25 shows an example in which one overlapping portion 65 is formed in which the end portions of the transmitted sound suppressing member 60 that covers the outer surface of the member that becomes the transmitted sound source 80 overlap each other. In FIG. 26, the two transmitted sound suppression members 60 are used to cover the outer surface of the member that becomes the transmitted sound source 80, and two overlapping portions 65 are formed in which the ends of the two transmitted sound suppression members 60 overlap each other. Is shown as an example.

  25 and 26, when the transmitted sound suppressing member 60 covers the outer surface of the member that becomes the transmitted sound source 80, the overlapping portion 65 is fixed with the band 71, the clip 72, or the stapler 73, and the transmitted sound suppressing member 60 is fixed. It can attach so that the outer surface of the member used as the permeation | transmission sound source 80 may be covered. The transmission sound suppressing member 60 is fixed by the band 71, the clip 72, or the stapler 73 when the transmitted sound source 80 of the transmitted sound suppressing member 60 is projected when the transmitted sound suppressing member 60 covers the outer surface of the member that becomes the transmitted sound source 80. The position is set to avoid the region R2. This is because if the band 71, the clip 72, or the stapler 73 is installed in the projection region R2, the air chamber of the sound absorbing material 61 constituting the transmitted sound suppressing member 60 may be crushed.

  As described above, the transmitted sound suppressing member 60 can be attached to the outer surface of the member to be the transmitted sound source 80 in a state where the air chamber of the sound absorbing material 61 of the transmitted sound suppressing member 60 is secured. The sound energy attenuation effect of 61 can be ensured.

  25 and 26, the transmitted sound suppression member 60 shown in FIGS. 12 and 13 is shown as a representative example, but the transmitted sound suppression member 60 may be the one shown in FIGS. 14 and 15 may be used, or those shown in FIGS. 16 and 17 may be used. The fixing member 70 (including the band 71, the clip 72, or the stapler 73) is not limited to the exemplified members as long as it can fix the transmitted sound suppressing member 60.

<Effects of refrigeration cycle apparatus 100>
In the refrigeration cycle apparatus 100, the compressor 1, the first heat exchanger (heat source side heat exchanger) 3, the expansion device 5, and the second heat exchanger (use side heat exchanger) 6 are connected by a refrigerant pipe 15. The refrigerant circuit includes a refrigerant that changes in two phases, and the refrigerant flows through the refrigerant circuit including the refrigerant pipe 15. The transmitted sound suppressing member 60 is disposed on the outer surface.

  Therefore, according to the refrigeration cycle apparatus 100, since the transmitted sound suppression member 60 is disposed on the outer surface portion of the refrigerant circuit where the refrigerant changes phase, the transmitted sound suppression member 60 is caused by the state of the refrigerant flowing in the refrigerant pipe 15. Thus, it is possible to suppress the permeation sound transmitted from the inside of the refrigerant pipe 15 to the outside of the refrigerant pipe 15, and as a result, it is possible to reduce the refrigerant flow noise.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 absorbs audible band sound and ultrasonic band sound.
Therefore, according to the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 can take measures against both transmitted sound in the audible band and transmitted sound in the ultrasonic band.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is disposed in at least one of a branch portion of the refrigerant pipe 15 and a bent portion of the refrigerant pipe 15 that constitute the refrigerant circuit.
Therefore, according to the refrigeration cycle apparatus 100, since the transmitted sound suppression member 60 is disposed in at least one of the branch part of the refrigerant pipe 15 and the bent part of the refrigerant pipe 15 where the phase state of the refrigerant changes, the refrigerant undergoes a phase change. It is possible to effectively reduce the refrigerant flow noise generated at the time.

In the refrigeration cycle apparatus 100 using the electronic expansion valve 5X as the expansion device 5, the transmitted sound suppression member 60 is disposed in the electronic expansion valve 5X constituting the refrigerant circuit.
Therefore, according to the refrigeration cycle apparatus 100, since the transmitted sound suppression member 60 is disposed in the electronic expansion valve 5X in which the phase state of the refrigerant changes, it is possible to effectively reduce the refrigerant flow noise that occurs when the phase of the refrigerant changes. .

The refrigeration cycle apparatus 100 uses the rectifying pipe 5Y as the expansion device 5, and the transmitted sound suppression member 60 is disposed in the rectifying pipe 5Y constituting the refrigerant circuit.
Therefore, according to the refrigeration cycle apparatus 100, since the transmitted sound suppression member 60 is arranged in the rectifying pipe 5Y where the phase state of the refrigerant changes, it is possible to effectively reduce the refrigerant flow noise generated when the refrigerant changes phase.

The refrigeration cycle apparatus 100 includes a distributor 4X on at least one inlet side of the first heat exchanger (heat source side heat exchanger) 3 and the second heat exchanger (use side heat exchanger) 6, and transmits The sound suppression member 60 is disposed in the distributor 4X constituting the refrigerant circuit.
Therefore, according to the refrigeration cycle apparatus 100, since the transmitted sound suppression member 60 is disposed in the distributor 4X in which the phase state of the refrigerant changes, it is possible to effectively reduce the refrigerant flow noise generated when the refrigerant undergoes a phase change.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 covers the entire circumference of the arrangement location.
Therefore, according to the refrigeration cycle apparatus 100, it is possible to suppress sound radiation that propagates radially from the entire circumference of the arrangement location to the outside.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is constituted by a sound absorbing material 61 including an air chamber.
Therefore, according to the refrigeration cycle apparatus 100, the transmitted sound can be effectively absorbed by the air chamber of the sound absorbing material 61.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is composed of two layers of a sound absorbing material 61 including an air chamber and a vibration damping material 62 including a dielectric material. Constitutes the outermost side of the transmitted sound suppressing member 60.
Therefore, according to the refrigeration cycle apparatus 100, sound absorption and sound insulation can be achieved under a thickness condition thinner than the conventional thickness.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is composed of two layers of a sound absorbing material 61 including an air chamber and a sound insulating material 63 including a dielectric material. The outermost side of the sound suppressing member 60 is configured.
Therefore, according to the refrigeration cycle apparatus 100, sound absorption and sound insulation can be achieved under a thickness condition thinner than the conventional thickness.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 has three layers of a sound absorbing material 61 including an air chamber, a sound insulating material 63 including a dielectric material, and a vibration damping material 62 including a dielectric material. The layer made of the damping material 62 constitutes the innermost side of the transmitted sound suppressing member 60, the layer made of the sound insulating material 63 constitutes the outermost side of the transmitted sound suppressing member 60, and the layer made of the sound absorbing material 61 A layer formed by the material 62 and a layer formed by the sound insulating material 63 are formed.
Therefore, according to the refrigeration cycle apparatus 100, sound absorption and sound insulation can be achieved under a thickness condition thinner than the conventional thickness.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is attached using an adhesive material.
Therefore, according to the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure.

In the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 is attached using a fixing member 70.
Therefore, according to the refrigeration cycle apparatus 100, the transmitted sound suppression member 60 can be attached without requiring a complicated process and a complicated structure.

In the refrigeration cycle apparatus 100, the fixing member 70 fixes the transmitted sound suppression member 60 at a position where the transmission sound source 80 of the transmitted sound suppression member 60 avoids the projection area (projection area R 1, projection area R 2).
Therefore, according to the refrigeration cycle apparatus 100, since the air chamber of the sound absorbing material 61 constituting the transmitted sound suppression member 60 in the projection region R1 and the projection region R2 is not crushed by the fixing member 70, the sound absorption by the sound absorbing material 61 is eliminated. The characteristics do not deteriorate.

In addition, according to the electrical equipment according to the present invention, since the refrigeration cycle apparatus is provided, it is possible to take measures against unpleasant noise generated from electrical equipment familiar to consumers, and to reduce consumer discomfort. it can.
In addition, as an electric equipment, an air conditioning apparatus, a hot-water supply apparatus, a freezing apparatus, a dehumidification apparatus, or a refrigerator is mentioned, for example.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 flow-path switching apparatus, 3rd 1st heat exchanger, 1st distributor, 4X distributor, 4X-1 mixing flow path, 5 expansion device, 5X electronic expansion valve, 5Y rectifier tube, 6th 2 heat exchangers, 7 second distributor, 15 refrigerant pipe, 15A first pipe, 15AX first pipe, 15BX second pipe, 15X refrigerant pipe, 16 first blower, 17 second blower, 51X main body, 52X valve body , 52aX cylindrical part, 52bX conical part, 53X valve seat, 54X throttle part, 55X valve chamber, 56X through hole, 57X through hole, 59X drive device, 60 transmitted sound suppression member, 61 sound absorbing material, 62 damping material, 63 sound insulation material, 65 overlapping part, 70 fixing member, 71 band, 72 clip, 73 stapler, 80 transmission sound source, 100 refrigeration cycle apparatus, 100A heat source side unit, 100B Load side unit, R1 projection area, R2 projection area.

The refrigeration cycle apparatus according to the present invention includes a refrigerant circuit in which a compressor, a first heat exchanger, an expansion device, and a second heat exchanger are connected by a refrigerant pipe, and the refrigerant circuit has a refrigerant that changes in two phases. And the refrigerant flows through the refrigerant circuit including the refrigerant pipe, and is connected to a branch portion of the refrigerant pipe, a bent portion of the refrigerant pipe, the expansion device, and the expansion device. A transmission sound suppression member is disposed on at least one outer surface of the refrigerant pipe, and the transmission sound suppression member is made of a sound absorbing material including an air chamber and absorbs an audible band sound and an ultrasonic band sound. It is.

Claims (13)

Comprising a refrigerant circuit in which a compressor, a first heat exchanger, an expansion device, and a second heat exchanger are connected by refrigerant piping;
The refrigerant circuit is filled with a two-phase changing refrigerant, and the refrigerant flows through the refrigerant circuit including the refrigerant pipe,
A refrigeration cycle apparatus in which a transmitted sound suppression member is disposed on at least one outer surface of the refrigerant pipe connected to the branch part of the refrigerant pipe, the bent part of the refrigerant pipe, the expansion device, and the expansion device. The transmitted sound suppressing member is
The refrigeration cycle apparatus according to claim 1, which absorbs an audible band sound and an ultrasonic band sound. The refrigeration cycle apparatus according to claim 1, wherein the expansion device is an electronic expansion valve or a rectifying pipe. A distributor on at least one inlet side of the first heat exchanger and the second heat exchanger;
The transmitted sound suppressing member is
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein the refrigeration cycle apparatus is also disposed on an outer surface of the distributor. The transmitted sound suppressing member is
The refrigeration cycle apparatus according to any one of claims 1 to 4, which covers the entire circumference of the arrangement location. The transmitted sound suppressing member is
The refrigeration cycle apparatus according to any one of claims 1 to 5, comprising a sound absorbing material including an air chamber. The transmitted sound suppressing member is
A sound absorbing material including an air chamber;
It consists of two layers, a damping material containing a dielectric material,
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the layer made of the damping material constitutes the outermost side of the transmitted sound suppression member. The transmitted sound suppressing member is
A sound absorbing material including an air chamber;
It is composed of two layers, a sound insulating material containing a dielectric material,
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein a layer of the sound absorbing material constitutes the outermost side of the transmitted sound suppressing member. The transmitted sound suppressing member is
A sound absorbing material including an air chamber;
A sound insulating material containing a dielectric material;
It consists of three layers: a damping material containing a dielectric material,
The layer made of the damping material constitutes the innermost side of the transmitted sound suppressing member, the layer made of the sound insulating material constitutes the outermost side of the transmitted sound suppressing member, and the layer made of the sound absorbing material is a layer made of the damping material The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the refrigeration cycle apparatus is configured between the sound insulating material and the layer. The transmitted sound suppressing member is
The refrigeration cycle apparatus according to any one of claims 1 to 9, wherein the refrigeration cycle apparatus is attached using an adhesive material. The transmitted sound suppressing member is
The refrigeration cycle apparatus according to any one of claims 1 to 9, wherein the refrigeration cycle apparatus is attached using a fixing member. The fixing member is
The refrigeration cycle apparatus according to claim 11, wherein the transmitted sound suppression member is fixed at a position avoiding a projection area of the transmitted sound source of the transmitted sound suppression member. An electrical apparatus comprising the refrigeration cycle apparatus according to any one of claims 1 to 12.

Images